Automatic speed-varying mechanism



June 26, 1934. A. K. ANTONSEN 1,964,494

AUTOMATIC SPEED VARYING MECHANISM Filed March 19, 1951 5 Sheets-Sheet H INVENTOR W H/v/rn? K. filvm/vsz/v A. K. ANTONSEN AUTOMATIC SPEED VARYING MECHANISM Filed March 19, 1931 June 26, 1934.

5 Sheets-Sheet I5 INVENTOR ATTOR N EY June 26, 1934. ANTONSEN 1,964,494

AUTOMATIC SPEED VARYING MECHANISM Filed March 19, 1931 5 Sheets-Sheet 4 5 a C A INVENTOR.

ANKER K. HNTONSEN BY 2/ I ATTORNEY.

June 1934- A. K. ANTONSEN AUTOMATIC SPEED VARYING' MECHANISN Filed March 19, 1931 5 Sheets-Sheet 5 INVENTOR. ANKER K. IQNTONSEN A TTORNEY.

Patented June 26, 1934 UNITED STATES PATENT OFFICE Anker K. Antonsen, Beloit, Wis., assignor to Fairbanks, Morse & Co., Chicago, Ill., a corporation of Illinois Application March 19,

12 Claims.

This invention relates to improvements in automatic speed-varying mechanism, and more particularly to an improved assembly for effecting selective controlling cyclic motion and speed control means for internal combustion engines employed in connection with well drilling apparatus.

In the drilling of wells by the usual standard or cable system, it is known in the art, that the drilling motion is intermittent, and the load on the prime mover may fluctuate, in a very brief time, from no-load to full-load. It is thus apparent that, unless suitable provision be made, the engine may tend to accelerate to a point be- I yond the speed of the falling tools with obvious disadvantages. These disadvantages are eliminated by the use of the present speed control assembly which provides, in addition, several novel features.

Particularly when an internal combustion engine is employed as a prime mover in connection with well drilling apparatus, it has been difficult to regulate satisfactorily, the speed of the internal combustion engine to affect the requisite drilling motion and at the same time with the same control apparatus, to secure the proper degree of engine speed control for fishing, bailing, pulling, and the like. This difficulty has prevailed, particularly, in the case of internal combustion engines employing mechanical injection of fuel, and it is for the control of this class of engines, that the present improved assembly is particularly adapted.

The present invention constitutes certain modifications of and improvements with respect to the device covered by Letters Patent No. 1,919,449, to George Oetzel, issued July 25, 1933.

An object of the present invention is to provide an improved control device for internal combustion engines employed in connection with well drilling apparatus, in which the speed of the engine is controlled in such a manner as to insure the most desirable motion of the drilling tools, and which further effects an almost instantaneous response of the engine speed control appa ratus, to the several different positions of a band wheel or equivalent member associated with well drilling apparatus.

An additional object is the provision of an improved assembly including an internal combustion engine, drilling apparatus and control means so associated with the engine and apparatus as toprovide the maximum flexibility and convenience of speed and drilling motion control, with 1931, Serial No. 523,760

a minimum number of parts, and a minimum number of remote control connections.

Additional objects of the invention will appear by reference to the above mentioned copending application, and from the following detailed description of parts of an assembly constructed in accordance with the present invention, and the drawings accompanying this application, in which:

Fig. l is a diagrammatic elevation of a preferred arrangement of drilling assembly, to which certain of the present improvements are applied; Fig. 2 is a vertical section of a manual control assembly employed in connection with the present preferred device; Fig. 3 is a section along line 33 of Fig. 2; Fig. 4 is a vertical section showing a preferred form of governor and. governor case; Fig. 5 is a fragmentary end elevation of the structure appearing in Fig. 4, with certain parts removed for clearness; Fig. 6 is a plan view of certain parts of the assembly apearing in Fig. 4, Fig. 6 being shown partly in section and partly in elevation, the section portion thereof being taken partially along the line 66 of Fig. '7; Fig. 7 is a fragmentary sectional elevation as viewed along line 77 in Fig. 4; Fig. 8 is a section taken along line 88 of Fig. 4; Fig. 9 is an enlarged front elevation of the preferred form of control assembly; Fig. 10 is an enlarged fragmentary section taken along line 1010 in Fig. 9; Figs. 11 and 12 are diagrammatic views of the operating linkage system and controls therefor, I

showing the external low speed and high speed cyclic positions, respectively, and Fig. 13 is a diagrammatic view of a portion of the operating linkage system and the controls therefor, showing the position of the controls for ,no cyclic movement of the linkage.

Referring by characters of reference to the drawings, the drilling aparatus (Fig. 1) includes a walking beam 10, which is pivotally mounted intermediate its ends, on a post 11. From one end of the beam 10 is suspended a string of drilling tools (not shown) by means of a cable 12, which extends downwardly into a drill hole 90. The opposite end of the beam is operatively connected to a rotatable band wheel 13, by means of a crank or equivalent connection 14, which serves in a well known manner, to reciprocate the beam. as the band wheel is rotated. The band wheel is driven by means of a belt 15, or the equivalent, which engages a suitable pulley (not shown) on the crankshaft of an internal combustion engine, indicated generally at 16. As is known in the drilling art, the desired drilling motion of the band wheel and walking beam, is irregular, due to the fact that during a complete cyclic movement of the operating end of the beam, the prime mover is subjected alternately to full-load operating conditions and practically to no-load operation. Failure properly to accelerate and decelerate the engine, may result, as is known, in difificulties, such as a broken cable, undesirable stretch in the cable, or inemcient drilling according to conditions encountered.

The present invention is adapted particularly for use in connection with internal combustion engines having variable stroke injection, the fuel and speed control features of such an engine being described in Letters Patent No. 1,852,132 issued to Edward '1. Adams, June '7, 1932. It will appear, however, as the description proceeds, that the desired assembly, including the governor may be applied to any usual form of prime mover.

It will appear obvious that in order to effect a cyclic speed control of the prime mover, it is necessary to coordinate the position of certain engine control elements, with the position of the band wheel 13 according to its relation to the walking beam 10, and the string of tools suspended from the cable 12. For the purpose of effecting this coordination, there is provided a control crank 17 on the band wheel shaft, with which is operatively associated a connecting rod 18, a bell crank lever 19 arranged to oscillate, as the band wheel rotates, about the fixed pivot 20. Motion from the lever 19 is in turn communicated, through a horizontally disposed connecting rod 21, to an enclosed control assembly, indicated generally at 22, which is mounted for convenience of location with respect to the drill hole, on a post such as a headache, or control post 23. Through the agency of suitable mechanism identified with the control assembly 22, and hereinafter more fully described, the oscil lating movement of the rod 21 is imparted to a double ended lever 24. The range of movement of this lever is, as will hereinafter appear, subject to control through the mechanism 22, the opposite ends of the lever 24 are connected, respectively, through a pair of control cables 25 and 26, to an engine control Wheel, 27, all as clearly appears in Fig. 1. For purposes of the present description it may be here noted that the movement of the lever 24 is an incomplete rotation or oscillation, which same movement is imparted to the wheel 27, which may be in turn, operatively connected through a belt or chain 28, with a separate sheave or wheel 29, on the governor case of the engine, and connected, as later appears, to certain of the governor elements.

Referring now to the details of constructions of the assembly, indicated generally at 22, this mechanism is, by preference, enclosed within a case 30, adapted to contain a suitable quantity of lubricant, and provided externally with a crank member, such as 31, (Figs. 1 and 9), arranged for oscillating movement with a shaft 32, (Fig. 2). This shaft serves, in turn, to carry a slotted lever 33, the slot therein being indicated at 34. In this slot is operatively disposed one end of an articulated connecting rod consisting in the present example, of a series of pivotally connected links 35, 36 and 37. To the free end of link 35, there is pivoted a roller 33 movably disposed within the slot 34, for a purpose hereinafter appearing. To the same free end of link 35, there is also connected a link 39 pivotally associated by means of apin 96 with a lever 40,

which is, in turn, secured to a control shaft 41 projecting to the outside of the case 30, the projecting portion being provided with a manual control lever 42 (Figs. 1 and 9) which may be provided with a suitable pointer 97 cooperating with a dial 91 on the case 30 to visibly indicate the operative position of the control. A control looking lever 98 (Figs. 9 and 10) is, by preference, threadedly associated with the shaft 41, so that the lever 42 and shaft 41 may be locked in any desired adjustable position.

The articulated rod consisting of links 35, 36 and 37 has its upper or outer end pivotally associated with a crank member 43 amxed to a shaft 44, which projects to a point exterior to the case 30, the projecting portion of the shaft serving to carry, and constitute an axis for, the double ended lever 24, above referred to. To the pivotal connection between the links 35 and 36, there is rotatably secured by means of a pin 99 a pivot link 45 having its inner end carried by a pivot pin 46 which is secured to the adjacent wall of the case 30. The provision of the link 45 serves to restrain and to a certain extent, to control the movement of the links 35 and 36. It will be readily seen that the movement of the pin 99 connecting links 35 and 36 is confined to an arc, the radius of which is the pivoted link 45.

It will appear from the foregoing description that the slotted member 33 is subjected, as the band wheel rotates, to an oscillating or rocking .rovement about the axis of the shaft 32. It wiil further appear that this movement is imparted, through the linkage 35, 36 and 37, to the shaft 44, (see Figs. 11 and 13), and hence to the governor or speed control device of the engine.

It will further appear that the effective stroke or range of movement of the member 34 exteriorly of the case 30, may be controlled through the provision of a rotatable control shaft 47, to which is affixed a control wheel 48, this shaft being provided with a threaded portion 49, by which there is carried a traveling nut 50 (Figs. 2 and 3). As the wheel 48 is rotated the nut 50 will obviously be moved endwise of the shaft 4'? in a direction depending upon the direction of movement of the control wheel, the nut being prevented from rotation with the shaft 4'7, through the provision of a guide 51, secured within the case. The nut 50 is provided with laterally projecting trunnions 52, which serve to receive and operatively engage a pair of control links 53, the opposite ends of these links being pivotally connected to a through pin 54, which constitutes also the pivotal connection between the links 36 and 37. Movement of the nut 50 between ends of the shaft 49 serves to shift the links 53 to the right or left, for purposes of changing the angularity of links 36 and 37, the limits of such movement being indicated 2.

by a comparison of Figs. 11 and 12. Such adjustment results in a change in angular position of the double-ended arm or lever 24; the lever 24 being connected to wheel 2'7, controlling the engine governor, it appears that the governor, hence the engine speed, may be varied accurately at any time through wheel 48.

The opposite extremes of control lever 42 appear in Figs. 11 and 13, with roller 38 at the extreme left of the slot 34, the roller and link 35 j ,1

will receive their greatest stroke from the rocker 33, while with the roller near the opposite end of the slot, the roller and link 35 are in what may be termed a no stroke position. In the former case, lever 44 will receive a maximum stroke, and in the latter, no oscillation whatever. It will appear from the foregoing description, that the connection from shaft 41 to the roller 38 enables, through manipulation of the manual control lever 42, a variation, at any time, in the range of movement of the lever 24, and hence of wheel 27, and hence the range of speeds through which the engine is varied during a given revolution of the band wheel 13. This feature of control may, for convenience, be referred to as the cyclic speed change, or cyclic movement since it occurs with regularity, but subject to full control.

In distinction from, and independently of the cyclic control, the manual control wheel 48 operating through the shaft 47 to move the pivot 54 to the right or left (Figs. 2, 11 and 12), serves to provide an instantaneous speed control, since the effect of this movement of the pivot 54 results in angularly rotating the shaft 44, and hence lever 24 and the wheel 27. This adjustment may take place either during a given cyclic movement, or at any time when the members 24 and 2'7 are not impressed with the cyclic movement of the band wheel, as is desirable when the assembly is employed for purposes of pulling, fishing, bailing or other operations apart from the usual drilling operations. It will be readily seen that the rotation of the wheel 48 is partially restrained by the action of the spring 92 which prevents any casual or undesired movement.

Proceeding now to a discussion of the means by which the positions and movements of the lever 24, and the corresponding position and movement of the wheel 27 are employed for engine speed control purposes, it will appear from Figs. 4 and 5 that the pulley 29 of the present example is mounted on a stud shaft 55. This shaft, together with the remainder of the governor mechanism, is mounted within a casing or housing 56, which is operatively associated with the engine 16, the shaft 55 projects into the interior of the case 56, which may, like the case 30, serve to contain a suitable quantity of lubricant. Due to the described motion of the wheel or pulley 27, which is also imparted to the pulley 29, through the connecting means 28, it will appear that the motLon of shaft 55 is normally an oscillating movement, when the above described cyclic movement is in operation. This movement is, in turn, imparted through a connecting rod 57 through a pivoted connection 58 to a movable fulcrum structure 59, which serves to slidably engage, through a movable roller 60, one side of a governor lever 61. As a means for insuring a straight line movement of the movable fulcrum 59, as it is oscillated or reciprocated by the rod 57, it is preferred to provide a pair of guide members 100 engaging opposite sides of the movable fulcum structure, this arrangement best appearing in Figs. 4 and 5. These guide members are secured to the casing 56. The lever 61 is, by preference, pivotally connected by means of a pin 79 to a link 101 which is pivotally dependent from the upper portion of the case, as shown at 62, this detail best appearing in Figs. 4, 6 and 7. It will be readily seen that the link 191 pivoted at 62 prevents any appreciable endwise movement of the lever 61.

The governor employed in the device of the present example is closely similar in principle, to that described in the above noted application of George Oetzel, and includes a hollow governor shaft 63, which is rotated by means of a gear 64 which, in turn; meshes with a gear 65, keyed to a shaft 66. The shaft 66 may consist of any suitable engine driven shaft, such as a lay shaft driven in timed relation with the crank shaft of the engine 16. The governor shaft 63 is provided with a forked portion 67, to which are pivotally attached weighted governor arms 68, by means of pins 69. The inner end portions of these arms are provided with rollers 70, which engage grooved portions 71, fixedly secured to a governor spindle 72, the spindle 72, as will appear from Fig. 4, is movable endwise, as the weighted arms are thrown outwardly, under centrifugal force, in a manner to cause the spindle to slide longitudinally. The inner end portion OI the governor spindle 72 is journaled in ball bear-ngs 73, carried by a collar 74, the collar, however, being prevented from rotation through the provision of a pin 75 carried by a stationary bearing arm 76 which is in turn supported by the case 56. The member 74 (Fig. 6) is provided with lateral trunnions or pivots 77, which serve n turn to carry a pair of spaced links 78 thepivot ends of which are connected through a pm or bolt 79, which also extends through the control lever 61 and link 101, as shown in Figs. 4, 6 and '7. As a means of opposing the endwise movement of the spindle 72 and the correspondmg movement of the pivot 79 and lever 61, there s provided a governor spring 80 operating as a tension spring. One end of the sprQng is anchored to the case as at 81, and the opposite end of the spring 80, is provided with a swivel connection 82 at its point of engagement with the lower or outer end of lever 61.

As a means of translating the endwise movementof the governor spindle 72 for purposes of effecting a controlling movement of the engine throttle, there is provided within the case a bearmg arm 83, an integral portion of which is extended upwardly to form a journaled portion 84. ThlS portion serves as a fulcrum for an angulate lever 85 in the nature of a bell crank the short arm of which is conveniently provided with rollers 86 operating within an annularly grooved collar 87 (Fig. 8) which is secured to the spindle 72. It will appear obvious, that the collar 87 moves endwise, in accordance with the movements of the spindle 72, and thus serves to rock the lever 85 about a pivot 102 within the portion 84. The free end of the lever 85 is suitably connected to certain of the engine control members (not shown). Since the lever 85 may be connected to an engine speed-control organizat on in a variety of ways, the specific connections beyond this lever form no part of the present invention. One form of such connection is shown and described in Patent No. 1,919,449 above cited, the material parts of which are in: corporated herein by this reference.

While the manner of use and operation of the described assemby is thought fully apparent from the foregoing detailed description of its parts, it may be briefly reviewed for sake of completeness. It will appear that the rotation of the band wheel 13 by the engine 16 operates, through the agency of the rod 21, and member 31, to oscillate the slotted member 33 within the assembly 22. The rocking movement of this irrilember is, in turn, imparted (Figs. 11 and 12) to through the shaft 44, lever 24 and the cables 25 and 26, to impart an oscillating movement to the interconnected wheel or pulley members 27 and 29. The degree of oscillating movement impart ed to the lever 24 may be visibly seen by the prodescribed linkage 35, 36 and 37, thence the band wheel 13.

ing full instantaneous speed control of the vision of a pointer on the lever which cooperates with a dial (Fig. 9) 95 on the case 30. The oscillating movement of the pulley 29 serves, through shaft 55 and link 57, to move the fulcrum 60 of lever 61, upwardly and downwardly, depending upon the extent of cyclic movement as controlled by the lever 42, with each rotation of the band wheel. Since the tension of spring is substantially constant, the effect of the different positions of the fulcrum structure 59 is to subject the spindle 72 to alternately greater and less opposition to its endwise movement under influence of the centrifugal members 68. This cyclic variation in effecting spring loading of the spindle '72 serves to cause a periodic controlling movement of the lever 85, and hence a cyclic control of the engine speed control members (not shown). The above cyclic movement is, however, predicated upon the position of the roller 38 (Fig. 2), in relation to the slot 34. This roller and hence the link 35 may be varied in any desired position through the manual actuation of the lever 42, the roller 38 may be actuated to a position (Fig. 13) with respect to the rocker 33, in which the roller operatively engages arcuate portions 103 of the slot 34, these portions being formed on arcs taken from the axis of the shaft 32. In this position the oscillating movement of the member 33 will be without effect in rotating shaft 44, and hence even though the engine and band wheel are in operation, there will be no cyclic control movenent imparted to the engine governor through the pulley 29. As however, the roller 38 is moved to the left (Fig. 2), under the influence :of the lever 42, a gradually increasing stroke is imparted to the linkage 35, 36 and 37, and hence,

as above described, to the movable fulcrum 59, thus effectively increasing the variation of the engine speed range within a given revolution of As a 1. cans for accomplishengine independently of the position of the lever 42, the control shaft 4'? serves, through the toggle action of links 36 and 37, to rotate the shaft 44,

thus positioning the lever 24, which serves correspondingly to rock the pulleys 2'7 and 29, hence the shaft 55, to establish a different position of the fulcrum 59 with respect to the lever 61. In th's manner the loading of spring 80 to which the governor spindle 72 is subjected, may be independently altered at any time, thus efiectively altering the instantaneous speed of the engine.

It will be evident, with the roller 38 in the position shown in Fig. 13, that by turning the hand wheel 48, the links 36 and 3'7 are moved so as to place the lever 24, either in one or the other of the extreme positions lying midway of the full and broken line positions of the lever 24 as indicated in Fi s. 11 and 12, or to any position between such extremes. Such movement results in a rotation of the arm 43, lever 24, and the pulley secured to the shaft 55 (Fig. 4). As the lever 24 is moved toward the extreme position of Fig. 11, the link 57 is actuated to move the fulcrum roller 60 toward the spring 80. Thus, the spring force opposing the centrifugal action of the governor weights 68 is reduced, causing a reduction in the speed of the engine.

The present application presents certain distinctions over the prior patent of George Oetzel, above referred to, in that the cyclic speed variation, as in the present case, is affected by a cyclic shifting of a fulcrum associated with the governor lever 61. In the former application, cyclic speed changes were affected by alternately subjecting the governor spring proper, to a greater or less load.

From the point of view of simplicity and economy of manufacture and assembly, the present invention requires only two control cables, such as 25 and 26, connecting the control assembly with the engine. The former structure, in order to provide full control of the engine from the headache or control post, required siX control cables with consequently greater expense and diffiiculty in maintaining proper adjustment and a'iignments between the prime mover and the remote control featiues of the apparatus.

According to the present invention an operator stationed. at the control post is afforded full control of the engine through the hand wheel 48 and the control lever 42 so that he may instantly change or nullify the cyclic speed movements incident to the various drilling operations, and at the same time is afforded full instantaneous speed control over the engine irrespective of the stroke imparted to the governor mechanism through the movements of the fulcrum 59.

It will be apparent that the mechanism housed in the casing 56 may be utilized to advantage as a s eed control assembly for internal combustion engines, and may serve in itself as a complete assemby for this purpose. For well drilling purposes it is only necessary to install a remote cyclic and speed control assembly identified as 22, which may be placed in proximity to the drill hole so as to enabl complete engine speed control at this point. It is therefore readily seen that the present arrangement is practical, efhcient, and economical for well drilling service.

It will, of course, be understood that the present detailed description of parts and the accompanying drawings relate to a preferred executional embodiment of the invention, and that substantial changes may be made in the described arrangement and construction of parts without departing from the full intended spirit and scope of the invention, as defined by the appended claims.

I claim as my invention:

1. In combination with an engine and apparatus driven thereby, mechanism for varying the speed of the engine responsively to varying requirements of the driven apparatus, said mechanism including a governor, a lever connected to the governor, and adapted for connection to the engine for the purpose of speed control, the governor being driven by the engine and including centrifugally actuated elements, a governor spring and a lever connecting the centrifugally actuated elements of the governor with said spring, a rocker member, reciprocating connections thereto from said driven apparatus, a displaceable fulcrum for said lever, and means connected between said rocker and said fulcrum and operable on the fulcrum for varying the proportionate length of the arms of said lever, responsively to actuation of said driven apparatus.

' 2. In combination with an engine and apparatus driven thereby, a device for effecting automatic fluctuations in speed coordinately with varying requiremei s of the driven apparatus, the device embodying a governor, a lever connected to the governor, and adapted for speedcon rol connection to the engine, the governor being driven by the engine and including a lever, centrifugal governor elements acting upon the lever and a spring engaging the lever in opposition to the centrifugal movement of the cen trifugal elements, a plurality of reciprocating m0- tion-transmitting elements actuated by said driven apparatus, one of the reciprocating elements being movable along and engaging said lever, and arranged for modifying the biasing effect of said spring and lever upon the centrifugal governor elements.

3. In combination with an engine and apparatus driven thereby, a centrifugal governor assembly driven by the engine, a lever connected to the governor, and adapted for speed-control connection with the engine, the governor including centrifugal elements, a governor spring and a lever connecting the centrifugal elements of the governor to the governor spring, a rocker, a connecting structure between the rocker and lever, including a fulcrum reciprocally movable along the lever, and reciprocating elements connecting said rocker and engine-driven apparatus.

l. In combination with an engine and reciprocating apparatus driven thereby, an engine speedcontrol assembly including a governor, a lever actuated thereby, and adapted for speed-control connection with the engine, the governor being driven by the engine and including a spring, centrifugal elements, a lever connected between the spring and centrifugal elements and a shiftable fulcrum for said lever, reciprocating mechanism operatively connecting said driven apparatus and fulcrum for shifting said fulcrum with respect to the lever, for effecting automatic cyclic changes in governor setting responsively to actuation of the driven apparatus, and means, including parts of said reciprocating mechanism, for shifting said fulcrum responsively to manual control' 5. A remote-control assembly for use in connection with drilling apparatus of a type including an internal combustion engine of variable speed type and a band wheel driven thereby, said assembly including a control mounting, a rocker carried thereby, an operative connection between the band wheel and rocker, a rock shaft carried by the mounting, a speed-varying connection from the rockshaft to the engine, an articulated structure connecting said rocker and rock shaft, means for manually varying the point of connection between said articulated structure and said rocker for controlling amplitude of movement of said rock shaft, and means for manually varying the angular relation between the parts of said articulated structure for the purpose of varying,

through the control connections, the speed of the engine.

6. In a remote control assembly for use in connection with drilling apparatus of a type including an engine, an engine governor and a band wheel driven by the engine, a casing, a rocker within said casing, a driving connection from the band wheel to said rocker arranged for imparting oscillating movement to said rocker, an oscillating shaft carried by said casing, control connections from said shaft to the engine governor, a jointed connecting rod between said rocker and said shaft, and means for manually varying the angularity of jointed parts of said connecting rod, whereby to adjust the angularity of said oscillating shaft for purposes of altering the setting of the engine governor.

'7. In a remote control assembly for use in connection with drilling apparatus of a type including an engine, an engine governor and a band wheel driven by the engine, a casing, a rocker within said casing, a motion transmitting connection from the rocker to the wheel for imparting oscillating movement to said rocker from rotation of said band wheel, an oscillating shaft carried by said casing, control connections from said shaft to the engine governor, a connecting rod of variable length between said rocker and said shaft, means for manually varying the effective length of said connecting rod, for altering through said control connections, the governor setting, and manual control means for varying the point of connection between said rod and said rocker, for controlling amplitude of movement of said oscillating shaft.

8. In a remote control assembly for use with drilling apparatus including an engine and a band wheel driven thereby, an engine governor, a control structure mounted remotely from the engine, a rocker carried by said structure, connecting means between the rocker and band wheel for oscillating said rocker responsively to rotation of the band wheel, a cyclic control shaft carried by the control structure, a control connection from the cyclic control shaft to the engine governor, members constituting a toggle joint for connecting said rocker and the control shaft, and means for manually varying the angular relation between the members constituting said toggle joint, whereby to vary the zone of actuation of the cyclic control shaft.

9. In a control assembly for use with drilling apparatus of a type including a variable-speed engine and a band wheel driven thereby, a control housing mounted at a distance from the engine, a rock shaft carried by the control housing, means connected to the rock shaft and driven by the band wheel for causing a cyclic actuation of the said rock shaft, a second rock shaft carried by the housing, a connection from the second rock shaft to engine speed varying elements, means within the housing operatively connecting said shafts, means carried by the housing and movable for manually varying the amplitude of movement of said second rock shaft, and additlonal manual means for varying the range or zone of movement of said second rock shaft irrespective of its amplitude of movement.

10. In a speed regulating mechanism for use with drilling apparatus of a type including an internal combustion engine of a variable speed type and a band wheel driven thereby, a structure defining a control station, a control housing carried by said structure, a rocker carried by the housing, means connected to the band wheel for causing a cyclic actuation of said rocker, a second rocker carried by the housing, an operative connection between the second rocker and speed varying elements of the engine, means within the housing operatively connecting said rockers, manual control means carried by the housing for controlling the range of movement imparted to said second rocker by said first rocker, additional manual control means and connections therefrom to the second rocker for effecting instantaneous speed control of the engine through said second rocker.

11. In an engine governor assembly, a rotatable governor drive shaft, a governor spindle having a portion axially movable within the governor shaft, a tension spring tending to oppose an endwise movement of said spindle, a lever pivoted near one end to said spring and pivoted to said spindle, a link having a fixed pivot near one end and secured to the lever near the opposite end thereof, a movable fulcrum for said lever, a manually controlled crank, a link connecting said crank and fulcrum, whereby movement of the crank serves relatively to displace said lever and said fulcrum.

tween the lever and said spring at the opposite end of the lever, and through which said spring is connected to the spindle, a swingable support for one end of the lever, a movable fulcrum for said lever, a manual control member and elements connecting said member and fulcrum for moving said fulcrum along said lever.

ANKER. K. ANTONSEN. 

